Engine balancer system

ABSTRACT

An engine balancer system is provided in which a balancer housing ( 17 ) disposed so as to face an oil pan beneath a crankshaft is formed by joining an upper housing ( 29 ) and a lower housing ( 30 ) via mating faces (P), and the height of the mating faces (P) is lower on a vehicle front side than on a vehicle rear side. Oil discharge holes ( 45   a,    46 ) for discharging oil that is within the balancer housing ( 17 ) are formed in the mating faces (P) on the higher side of the balancer housing ( 17 ) and in the upper housing ( 29 ) above the mating faces (P) on the lower side of the balancer housing ( 17 ). This enables the position of the oil discharge hole ( 45   a ) on the lower side to be as high as possible, thereby suppressing penetration of oil into the interior of the balancer housing ( 17 ) through the oil discharge hole ( 45   a ).

RELATED APPLICATIONS

This is a continuation application U.S. Ser. No. 11/900/967 filed Sep. 14, 2007, now U.S. Pat. No. 7,418,938 which is a continuation of U.S. Ser. No. 11/407,620, filed Apr. 20, 2006, now U.S. Pat. No. 7,270,104 B2, which is a continuation of U.S. Ser. No. 10/507,464, filed May 31, 2005, now U.S. Pat. No. 7,047,927 B2, which is a 35 U.S.C. 371 national stage filing of International Application PCT/JP03/02765 filed Mar. 10, 2003, which claims priority to Japanese Patent Application No. 2002-64877, filed Mar. 11, 2002, the contents of which are incorporated herein by reference.

FIELD OF THE INVENTION

The present invention relates to an engine balancer system having a balancer housing formed by joining an upper housing and a lower housing via mating faces, the balancer housing being disposed so as to face an oil pan beneath a crankshaft of an engine.

BACKGROUND ART

Such an engine balancer system is known from Japanese Patent Application Laid-open No. 2001-140985.

In this conventional balancer system, a balancer housing is formed by joining an upper housing and a lower housing, and oil within the balancer housing is discharged via oil discharge holes formed in mating faces of the two housings.

If an engine is mounted in a vehicle body with its cylinder axis inclined, since the mating faces of the upper housing and the lower housing of the balancer housing are also inclined, when oil within an oil pan is agitated there is a possibility that oil might penetrate into the interior of the balancer housing via an oil discharge hole formed in the mating faces on the lower side.

DISCLOSURE OF INVENTION

The present invention has been achieved under the above-mentioned circumstances, and it is an object thereof to suppress the penetration of oil into the interior of the balancer housing via the oil discharge hole even when the balancer housing is provided at an inclination relative to the horizontal direction.

In order to attain this object, in accordance with a first aspect of the present invention, there is proposed an engine balancer system having a balancer housing formed by joining an upper housing and a lower housing via mating faces, the balancer housing being disposed so as to face an oil pan beneath a crankshaft of an engine, and the balancer housing being inclined so that the height of the mating faces varies from one side to the other, wherein oil discharge holes for discharging oil that is within the balancer housing are formed in the mating faces on the higher side of the balancer housing and in the upper housing above the mating faces on the lower side of the balancer housing.

In accordance with this arrangement, since the oil discharge holes for discharging the oil that is within the balancer housing are formed in the mating faces of the upper housing and the lower housing on the higher side of the balancer housing and in the upper housing above the mating faces on the lower side of the balancer housing, oil can easily be discharged on the higher side of the balancer housing, and by setting the oil discharge hole on the lower side of the balancer housing at as high a position as possible, it is possible to suppress the penetration of oil into the interior of the balancer housing via the oil discharge hole.

Furthermore, in accordance with a second aspect of the present invention, in addition to the first aspect, there is proposed the engine balancer system wherein an angle between the lower housing and the mating faces on the lower side of the balancer housing is larger than an angle formed between the lower housing and the mating faces on the higher side of the balancer housing.

In accordance with this arrangement, since the inclination of the lower housing is shallow on the higher side of the balancer housing where it is difficult for oil to be discharged via the oil discharge hole, it becomes easy for oil to be discharged via the oil discharge hole, and since the inclination of the lower housing is steep on the lower side of the balancer housing where it is easy for oil to be discharged via the oil discharge hole, it is possible thereby to contribute to a reduction in the dimensions of the balancer housing.

Moreover, in accordance with a third aspect of the present invention, in addition to the first or second aspect, there is proposed the engine balancer system wherein the engine is mounted transversely with the crankshaft disposed along the lateral direction of a vehicle body, the higher side of the balancer housing faces the rear of the vehicle body, and the lower side of the balancer housing faces the front of the vehicle body.

In accordance with this arrangement, since the engine is mounted transversely and the higher side and the lower side of the balancer housing face the rear and the front of the vehicle body respectively, it is possible, due to the oil level tilting when the vehicle is accelerating forward, to discharge oil from the oil discharge hole on the higher side of the balancer housing, where it is difficult for oil to be discharged, thereby improving the forward acceleration performance of the vehicle.

Furthermore, in accordance with a fourth aspect of the present invention, in addition to any one of the first to the third aspects, there is proposed the engine balancer system wherein a baffle plate extending from a position lower than the mating faces to a higher position is provided in the lower housing on the higher side of the balancer housing.

In accordance with this arrangement, since the baffle plate extending from the position lower than the mating faces to the higher position is provided on the higher side of the balancer housing where the oil discharge hole is provided in the mating faces of the upper housing and the lower housing, even when the oil level within the oil pan is disturbed it is possible to prevent the oil from penetrating into the interior of the balancer housing via the oil discharge hole formed in the mating faces.

Moreover, in accordance with a fifth aspect of the present invention, in addition to the first aspect, there is proposed the engine balancer system wherein the engine is mounted transversely with the crankshaft disposed in the lateral direction of a vehicle body, the lower side of the balancer housing faces the rear of the vehicle body, and the higher side of the balancer housing faces the front of the vehicle body.

In accordance with this arrangement, since the engine is mounted transversely, the lower side of the balancer housing faces the rear of the vehicle body, and the oil discharge hole is formed in the upper housing above the mating faces on the lower side of the balancer housing, it is possible to suppress the penetration of oil into the interior of the balancer housing via the oil discharge hole even when the oil level is tilted while the vehicle is accelerating forward, thereby suppressing any degradation in the forward acceleration performance of the vehicle.

Furthermore, in accordance with a sixth aspect of the present invention, in addition to the first aspect, there is proposed the engine balancer system having the balancer housing facing the oil pan disposed beneath the crankshaft and having an oil discharge hole for discharging oil that is within the balancer housing formed in an upper face of the balancer housing, wherein the position of an oil outlet at the lower end of an oil return passage formed in an engine block and the position of the oil discharge hole of the balancer housing are displaced from each other.

In accordance with this arrangement, since the position of the oil outlet at the lower end of the oil return passage and the position of the oil discharge hole of the balancer housing are displaced from each other, it is possible to suppress the flow of oil, which has been discharged from the oil outlet of the oil return passage, into the interior of the balancer housing through the oil discharge hole of the balancer housing.

Moreover, in accordance with a seventh aspect of the present invention, in addition to the sixth aspect, there is proposed the engine balancer system wherein the oil discharge hole of the balancer housing is covered by a baffle plate, and the oil outlet of the oil return passage is disposed at a position that avoids the baffle plate.

In accordance with this arrangement, since the oil discharge hole of the balancer housing is covered by the baffle plate, it is possible to prevent oil from flowing into the interior of the balancer housing via the oil discharge hole. Moreover, since the oil outlet of the oil return passage is disposed at the position that avoids the baffle plate, it is possible to smoothly return to the oil pan the oil discharged via the oil outlet without interference from the baffle plate.

Furthermore, in accordance with an eighth aspect of the present invention, in addition to the seventh aspect, there is proposed the engine balancer system wherein an escape section is formed in the baffle plate, the escape section letting the oil discharged via the oil outlet of the oil return passage escape.

In accordance with this arrangement, since the escape section letting the oil discharged via the oil outlet of the oil return passage escape is formed in the baffle plate, it is possible by bringing the oil outlet closer to the baffle plate to suppress any increase in the dimensions of the engine, and to suppress interference by the baffle plate with the oil discharged via the oil outlet.

Moreover, in accordance with a ninth aspect of the present invention, in addition to the eighth aspect, there is proposed the engine balancer system wherein the escape section is formed between fastening parts via which the baffle plate is secured.

In accordance with this arrangement, since the escape section of the baffle plate is formed between the fastening parts via which the baffle plate is secured, it is possible to suppress any degradation in the rigidity of the fastening parts.

Furthermore, in accordance with a tenth aspect of the present invention, in addition to the ninth aspect, there is proposed the engine balancer system wherein an edge of the escape section of the baffle plate is bent downward.

In accordance with this arrangement, since the edge of the escape section of the baffle plate is bent downward, it is possible to smoothly guide the oil discharged via the oil outlet of the oil return passage to the oil pan and, moreover, improve the rigidity of the baffle plate.

A lower block 14 of embodiments corresponds to the engine block of the present invention, bolts 32 and 50 of the embodiments correspond to the fastening parts of the present invention, and first to third baffle plates 47 to 49 of the embodiments correspond to the baffle plate of the present invention.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 to FIG. 13 illustrate a first embodiment of the present invention;

FIG. 1 is a front view of an engine,

FIG. 2 is a sectional view along line 2-2 in FIG. 1,

FIG. 3 is a sectional view along line 3-3 in FIG. 2,

FIG. 4 is a sectional view along line 4-4 in FIG. 2,

FIG. 5 is a sectional view along line 5-5 in FIG. 3,

FIG. 6 is a view from arrowed line 6-6 in FIG. 2,

FIG. 7 is a view from arrowed line 7-7 in FIG. 2,

FIG. 8 is a sectional view along line 8-8 in FIG. 6,

FIG. 9 is a sectional view along line 9-9 in FIG. 6,

FIG. 10 is a sectional view along line 10-10 in FIG. 6,

FIG. 11 is a sectional view along line 11-11 in FIG. 6,

FIG. 12 is a sectional view along line 12-12 in FIG. 6, and

FIG. 13 is an enlarged view of a part 13 in FIG. 7.

FIG. 14 is a view, corresponding to FIG. 13, of a second embodiment of the present invention.

FIG. 15 is a view, corresponding to FIG. 3, of a third embodiment of the present invention.

FIG. 16 to FIG. 19 illustrate a fourth embodiment of the present invention; FIG. 16 is a view corresponding to FIG. 3, FIG. 17 is a sectional view along line 17-17 in FIG. 16, FIG. 18 is a view from the reverse side of FIG. 17, and FIG. 19 is a sectional view along line 19-19 in FIG. 17.

FIG. 20 is a view, corresponding to FIG. 19, of a fifth embodiment of the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION

A first embodiment of the present invention is explained below with reference to FIG. 1 to FIG. 13.

As shown in FIG. 1, an outer shell of a vehicular four cylinder inline engine E is formed by stacking, from the top to the bottom, a head cover 11, a cylinder head 12, a cylinder block 13, a lower block 14, and an oil pan 15. A crankshaft 20 is disposed along the lateral direction of the vehicle body, and a cylinder axis L is inclined toward an exhaust side (the front of the vehicle body) relative to the vertical direction. A secondary balancer system 16 fixed to a lower face of the lower block 14 and housed within the oil pan 15 includes a driven balancer shaft 18 and a follower balancer shaft 19, which are supported in a balancer housing 17. A sprocket 21 provided at a shaft end of the crankshaft 20, which is supported between the cylinder block 13 and the lower block 14, is connected via an endless chain 23 to a sprocket 22 provided at a shaft end of the driven balancer shaft 18.

As shown in FIG. 2 to FIG. 5, four pistons 25 are slidably fitted in four cylinder bores 24 provided in the cylinder block 13, and are connected to four pins 20 a of the crankshaft 20 via connecting rods 26. Five bearing caps 27 are fitted within the lower block 14 and are each secured to a lower face of the cylinder block 13 via two bolts 28. Five journals 20 b of the crankshaft 20 are rotatably supported between the cylinder block 13 and the five bearing caps 27.

The balancer housing 17 of the secondary balancer system 16 is formed by joining an upper housing 29 and a lower housing 30 via eleven bolts 31, 32, 34 a, and 34 b, and further joining a pump housing 35 to end portions of the upper housing 29 and the lower housing 30 via a plurality of bolts 36. An upper wall portion 30 b is formed in an end portion of the lower housing 30 on the pump housing 35 side so as to extend over an upper face side of the balancer housing 17, and this upper wall portion 30 b is sandwiched between the upper housing 29 and the pump housing 35. A slit-shaped opening a (FIG. 6, FIG. 8, and FIG. 9) is formed between the upper housing 29 and the upper wall portion 30 b of the lower housing 30.

The three bolts 31 disposed so as to sandwich the driven balancer shaft 18 and the follower balancer shaft 19 therebetween are inserted from the upper housing 29 side and secured to the lower housing 30. The two bolts 32 disposed outside the driven balancer shaft 18 and the two bolts 31 disposed outside the follower balancer shaft 19 are inserted from the upper housing 29 side and secured to the lower housing 30. The two bolts 34 a inserted into the pump housing 35 at one end of the balancer housing 17 run through one of the bearing caps 27 and are secured to the lower face of the cylinder block 13, and the two bolts 34 b inserted from the lower housing 30 side at the other end of the balancer housing 17 run through the upper housing 29 and one of the bearing caps 27 and are secured to the lower face of the cylinder block 13.

The upper housing 29 is supported on the bearing caps 27 via four mounts 29 a through which the four bolts 34 a and 34 b run, thereby forming a gap β (see FIG. 4) between an upper face of the upper housing 29 and lower faces of the bearing caps 27. Ribs 600 which extend parallel to each other are formed on an upper surface of the balancer housing 17 to connect between the mounts 29 a.

The structure of the secondary balancer system 16 is now explained further with reference to FIG. 6 to FIG. 13.

As is clear from FIG. 8, the driven balancer shaft 18 of the secondary balancer system 16 is provided with, going from one end to the other, the sprocket 22, a first journal 18 a, a driven gear 18 b, a first balancer weight 18 c, a second journal 18 d, and a second balancer weight 18 e. The first and second journals 18 a and 18 d are sandwiched and supported between the upper housing 29 and the lower housing 30. As is clear from FIG. 9, the follower balancer shaft 19 of the secondary balancer system 16 is provided with, going from one end to the other, a first journal 19 a, a follower gear 19 b, a first balancer weight 19 c, a second journal 19 d, and a second balancer weight 19 e. The first and second journals 19 a and 19 d are sandwiched and supported between the upper housing 29 and the lower housing 30.

An oil pump 41 (see FIG. 9) is provided at the one end of the follower balancer shaft 19, which projects into the interior of the pump housing 35. The oil pump 41 is a known trochoidal pump, and includes an inner rotor 42 fixed to the follower balancer shaft 19 and an outer rotor 43 rotatably supported by the pump housing 35 and meshing with the inner rotor 42. A strainer 44 is provided on a lower face of the lower housing 30 at a position below an oil level O of oil that is held in the oil pan 15, and the strainer 44 is connected to a suction port 41 a of the oil pump 41 via an oil passage 30 a (see FIG. 12) formed integrally with the lower face of the lower housing 30. The strainer 44 is formed from a strainer element 44 a for filtering out foreign matter in the oil and a strainer cover 44 b covering the strainer element 44 a. A discharge port 41 b of the oil pump 41 is connected to a main gallery 13 a (see FIG. 3 and FIG. 4) of the cylinder block 13 via an oil passage (not illustrated).

Formed in the upper housing 29 are a pair of openings 29 b facing the driven gear 18 b and the follower gear 19 b, a pair of openings 29 c facing the first balancer weights 18 c and 19 c, and a pair of openings 29 d facing the second balancer weights 18 e and 19 e. By providing these openings 29 b, 29 c, and 29 d it is possible to prevent a trajectory T (see FIG. 3) of the lower end of the connecting rods 26 from interfering with an upper face of the upper housing 29, thus enabling the engine E to be reduced in size. Formed on an end face of the balancer housing 17 on the side opposite to the pump housing 35 are openings 17 a and 17 b (see FIG. 10) facing shaft ends of the driven balancer shaft 18 and the follower balancer shaft 19, the openings 17 a and 17 b extending over the upper housing 29 and the lower housing 30. These openings 17 a and 17 b are used when machining the interior of the balancer housing 17 so as to form supports for the first and second journals 18 a, 19 a, 18 d, and 19 d of the driven balancer shaft 18 and the follower balancer shaft 19. The inner diameters of the openings 17 a and 17 b are slightly larger than outer diameters of the first and second journals 18 a, 19 a, 18 d, and 19 d.

Four oil discharge holes 45 a to 45 d are formed in an end portion of the upper housing 29 on the driven balancer shaft 18 side, the four oil discharge holes 45 a to 45 d opening on an upper face of the upper housing 29. Each of the oil discharge holes 45 a to 45 d is formed in an elongated shape extending along the axial direction of the crankshaft 20. One (or a plurality of) slit-shaped oil discharge hole 46 is formed in the end of the balancer housing 17 on the follower balancer shaft 19 side, the slit-shaped oil discharge hole 46 extending along mating faces of the upper housing 29 and the lower housing 30. The oil discharge holes 45 a to 45 d open in the direction of the cylinder axis L, and the oil discharge hole 46 opens in a direction orthogonal to the cylinder axis L. Because of the inclination of the cylinder axis L, the balancer housing 17 is inclined so that the driven balancer shaft 18 side (front side of the vehicle body) is low and the follower balancer shaft 19 side (rear side of the vehicle body) is high, but the oil discharge holes 45 a to 45 d on the driven balancer shaft 18 side and the oil discharge hole 46 on the follower balancer shaft 19 side are disposed at positions higher than the horizontal oil level O (see FIG. 3) of the oil that is held in the oil pan 15.

A substantially rectangular first baffle plate 47 is secured to an upper face of the end of the upper housing 29 on the driven balancer shaft 18 side via the two bolts 32, which also join the upper housing 29 and the lower housing 30. A substantially rectangular second baffle plate 48 is fixed via two bolts 33 to a bank-shaped boss 30 c projectingly provided on an outer wall of the lower housing 30. The second baffle plate 48 extends upward and rearward along the outer wall of the lower housing 30, and its upper end reaches a position higher than the upper end of the oil discharge hole 46. A large number of through holes 30 d (see FIG. 12 and FIG. 13) are formed in the bank-shaped boss 30 c, the through holes 30 d providing communication between an upper face and a lower face of the bank-shaped boss 30 c. A rectangular U-shaped third baffle plate 49 is fixed to the lower face of the lower block 14 via four bolts 50.

When the engine E is running, rotation of the crankshaft 20 is transmitted to the driven balancer shaft 18 via the sprocket 21, the endless chain 23, and the sprocket 22, and rotation of the driven balancer shaft 18 is transmitted to the follower balancer shaft 19 via the driven gear 18 b and the follower gear 19 b. Since the number of teeth of the sprocket 21 of the crankshaft 20 is set so as to be twice the number of teeth of the sprocket 22 of the driven balancer shaft 18, and the number of teeth of the driven gear 18 b is set so as to be equal to the number of teeth of the follower gear 19 b, the driven balancer shaft 18 and the follower balancer shaft 19 rotate in opposite directions to each other (see arrows A and B in FIG. 11 and FIG. 12) at a rotational speed that is twice the rotational speed of the crankshaft 20, and secondary vibration of the engine E is damped by the first and second balancer weights 18 c, 19 c, 18 e, and 19 e provided on the driven balancer shaft 18 and the follower balancer shaft 19.

While the engine E is running, since the crankshaft 20 splashes oil within the crankcase, the oil attempts to penetrate into the interior of the balancer housing 17 via the openings 29 b, 29 c, 29 d, 17 a, and 17 b. When the oil penetrates into the interior of the balancer housing 17, the oil is stirred by the driven gear 18 b, the follower gear 19 b, the first and second balancer weights 18 c, 19 c, 18 e, and 19 e, etc. and there is the problem that the stirring resistance increases. By discharging, via the oil discharge holes 45 a to 45 d and 46 of the balancer housing 17, the oil swept up by the driven gear 18 b, the follower gear 19 b, the first and second balancer weights 18 c, 19 c, 18 e, and 19 e, etc. of the driven balancer shaft 18 and the follower balancer shaft 19 rotating in the directions of arrows A and B in FIG. 11 so as to return it to the oil pan 15, an increase in the stirring resistance is prevented.

During this process, as shown in FIG. 10 to FIG. 12, since outer edges of the first and second baffle plates 47 and 48 and outer edges of cover portions 49 a and 49 b of the third baffle plate 49 are bent downward, the oil discharged via the oil discharge holes 45 a to 45 d and 46 is diverted downward and the oil can be returned smoothly to the oil pan 15.

The first baffle plate 47 and the second baffle plate 48 fixed to the balancer housing 17 and the third baffle plate 49 fixed to the lower block 14 prevent the oil level O of oil that resides within the oil pan 15 from being disturbed. Since at least portions of the first and third baffle plates 47 and 49 extend to positions that cover the oil discharge holes 45 a to 45 d of the balancer housing 17, when droplets of the oil splashed accompanying rotation of the crankshaft 20 are scattered within the crankcase, the droplets of oil are blocked by the first and third baffle plates 47 and 49, and it is thus possible to suppress their penetration into the interior of the balancer housing 17 via the oil discharge holes 45 a to 45 d. In this way, since the oil discharge holes 45 a to 45 d are covered by utilizing the existing first and third baffle plates 47 and 49, it is unnecessary to employ a special cover member for covering these oil discharge holes 45 a to 45 d, thus reducing the number of components and the number of assembly steps.

In particular, since the third baffle plate 49, which is rectangular U-shaped, is provided with a plurality of cover portions 49 a and 49 b, which cover the oil discharge hole 45 d and a part of the oil discharge hole 46, and with a cutout 49 c between the cover portions 49 a and 49 b, the cutout 49 c makes it possible to minimize any increase in weight of the third baffle plate 49 while enabling the oil discharge hole 45 d and the part of the oil discharge hole 46 to be covered by the cover portions 49 a and 49 b. Moreover, since two of the four bolts 50 for fixing the third baffle plate 49 to the lower block 14 are disposed at positions closer to the cover portions 49 a and 49 b than to the cutout 49 c, it is possible to increase the rigidity of the cover portions 49 a and 49 b and suppress vibration. Furthermore, since the cutout 49 c is provided at a position where it faces the second balancer weights 18 e and 19 e, which have a larger diameter than that of the second journals 18 d and 19 d of the driven balancer shaft 18 and the follower balancer shaft 19, it is possible to minimize any increase in the vertical dimension of the engine E.

Since the first baffle plate 47 in the role of a cover member covers the oil discharge holes 45 a to 45 c, which are a plurality of openings, and the third baffle plate 49 in the role of a cover member covers the oil discharge holes 45 d and 46, which are a plurality of openings, that is, a plurality of openings are covered by a single cover member in each case, it is possible to reduce the number of cover members.

Since the first baffle plate 47 and the third baffle plate 49, which cover the oil discharge holes 45 c and 45 d respectively provided to the side (in a direction orthogonal to the driven balancer shaft 18) of the first balancer weight 18 c and the second balancer weight 18 e provided on either side of the second journal 18 d, are provided independently as separate bodies, it is possible to suppress any increase in the dimensions of the first and third baffle plates 47 and 49 as cover members while avoiding a complicated arrangement for the connection of the first baffle plate 47 and the third baffle plate 49 in the area around the second journal 18 d.

Moreover, since the cylinder axis L is inclined toward the front of the vehicle body so that the front side of the balancer housing 17 is low and the rear side thereof is high, it is easy for oil to flow into the interior of the balancer housing 17 via the front side oil discharge holes 45 a to 45 d, but since the front side oil discharge holes 45 a to 45 d are formed at positions higher than the mating faces P of the upper housing 29 and the lower housing 30, that is, formed so as to run through an upper wall of the upper housing 29, it is possible to prevent effectively the inflow of oil via the oil discharge holes 45 a to 45 d. On the other hand, since the rear side oil discharge hole 46 is at a high position, even when the oil discharge hole 46 is formed in the mating faces P of the upper housing 29 and the lower housing 30, thus simplifying the structure, there is no possibility of a large amount of oil flowing in therethrough.

As is clear from FIG. 12, an angle θ1, which is formed between the lower housing 30 and the mating faces P of the upper housing 29 and the lower housing 30 on the side (the rear side of the vehicle body) where the balancer housing 17 is high, is smaller than an angle θ2, which is formed between the lower housing 30 and the mating faces P on the side (the front side of the vehicle body) where the balancer housing 17 is low. That is, the inclination of an inner face of the lower housing 30 is shallow on the rear side of the vehicle body where it is difficult for oil to be discharged because the position of the oil discharge hole 46 is high, and in contrast the inclination of the inner face of the lower housing 30 is steep on the front side of the vehicle body where it is easy for oil to be discharged because the position of the oil discharge hole 46 is low. Therefore, when the oil level is inclined from the normal position O to a position O′ during forward acceleration of the vehicle, it is also possible to discharge effectively oil that is within the balancer housing 17 via the oil discharge hole 46, which is at a high position on the rear side of the vehicle body.

Moreover, since the inclination of the lower housing 30 is steep on the side where the balancer housing 17 is low (the front side of the vehicle body), it is possible to contribute to a reduction in the dimensions of the balancer housing 17 by bringing the lower housing 30 closer to the driven balancer shaft 18 in that area.

Furthermore, since the upper end of the second baffle plate 48 reaches a position higher than the upper end of the oil discharge hole 46, even when the oil level within the oil pan 15 is disturbed, it is possible to prevent oil from penetrating into the interior of the balancer housing 17 via the oil discharge hole 46. Furthermore, even when oil flows in between the outer wall of the lower housing 30 and the second baffle plate 48, the oil can be returned to the oil pan 15 via the through holes 30 d formed in the boss 30 c of the lower housing 30.

A second embodiment of the present invention is now explained with reference to FIG. 14.

In the first embodiment shown in FIG. 13, the second baffle plate 48 is fixed to the one bank-shaped boss 30 c provided on the outer wall of the lower housing 30 via the bolts 33, but in the second embodiment a second baffle plate 48 is fixed, via bolts 33, to two bosses 30 c provided on an outer wall of a lower housing 30, the two bosses 30 c being separated from each other. A gap δ is therefore formed between the two bosses 30 c, the outer wall of the lower housing 30, and the second baffle plate 48. Oil that has flowed in between the outer wall of the lower housing 30 and the second baffle plate 48 is returned to the oil pan 15 via the gap δ.

A third embodiment of the present invention is now explained with reference to FIG. 15.

As is clear from comparing FIG. 15 with FIG. 3 (the first embodiment), in the third embodiment a driven balancer shaft 18 side of a balancer housing 17 faces the rear of a vehicle body, and a follower balancer shaft 19 side thereof faces the front of the vehicle body. Therefore, even when the oil level on the driven balancer shaft 18 side rises during forward acceleration of the vehicle, since oil discharge holes 45 a to 45 d on the driven balancer shaft 18 side are formed in an upper face of the balancer housing 17, it is difficult for oil to penetrate into the interior of the balancer housing 17 via the oil discharge holes 45 a to 45 d, and it is possible to suppress degradation of the forward acceleration performance of the vehicle. If the oil discharge holes 45 a to 45 d on the low side of the balancer housing 17 are provided at positions higher than mating faces on the high side of the balancer housing 17, degradation of the forward acceleration performance of the vehicle is yet further advantageously suppressed.

A fourth embodiment of the present invention is now explained with reference to FIG. 16 to FIG. 19.

As is clear from a comparison of FIG. 6 and FIG. 11 (the first embodiment) with FIG. 16 and FIG. 17 (the fourth embodiment), whereas the second baffle plate 48 of the first embodiment is fixed via the two bolts 33 to the bank-shaped boss 30 c projectingly provided on the outer wall of the lower housing 30, a second baffle plate 48 of the fourth embodiment is secured to an upper face of the end on a follower balancer shaft 19 side of an upper housing 29 via two bolts 33, which also join the upper housing 29 and a lower housing 30.

A first baffle plate 47 and the second baffle plate 48 fixed to a balancer housing 17 and a third baffle plate 49 fixed to a lower block 14 prevent an oil level O of oil held within an oil pan 15 from being disturbed. Since at least parts of the first to the third baffle plates 47 to 49 extend to positions where they cover oil discharge holes 45 a to 45 d and 46 of the balancer housing 17, when droplets of oil splashed accompanying rotation of a crankshaft 20 are scattered within a crankcase, the droplets of oil are blocked by the first to the third baffle plates 47 to 49, and it is thus possible to suppress their penetration into the interior of the balancer housing 17 via the oil discharge holes 45 a to 45 d and 46. In this way, since the oil discharge holes 45 a to 45 d and 46 are covered by utilizing the existing first to third baffle plates 47, 48, and 49, it is unnecessary to employ a special cover member for covering these oil discharge holes 45 a to 45 d and 46, thus reducing the number of components and the number of assembly steps.

Formed in a cylinder block 13 and the lower block 14 are two oil return passages 13 b and two oil return passages 14 a for returning to the oil pan 15 oil that has lubricated a valve operating mechanism, etc. within a cylinder head 12. An oil outlet 14 b at the lower end of one of the oil return passages 14 a of the lower block 14 faces a cutout-shaped escape section 47 a formed by indenting the outer edge of the first baffle plate 47 in a semicircular shape. An oil outlet 14 b at the lower end of the other oil return passage 14 a of the lower block 14 faces a cutout-shaped escape section 49 d formed by indenting the outer edge of the third baffle plate 49 in a semicircular shape. Since the escape sections 47 a and 49 d are cutout-shaped and are formed by indenting in a semicircular shape, the molding thereof is easy. Reference numerals 13 c and 14 c in FIG. 19 denote a breather passage.

As is most clearly shown in FIG. 17, since the oil outlet 14 b of the one of the oil return passages 14 a is at a position that is offset from the oil discharge holes 45 a and 45 b that are the closest thereto, the oil outlet 14 b of the other oil return passage 14 a is at a position that is offset from the oil discharge hole 45 d that is the closest thereto and, moreover, these oil discharge holes 45 a, 45 b, and 45 d are covered by the first and third baffle plates 47 and 49, it is possible to prevent effectively the oil that has dropped via the oil outlets 14 b from flowing into the interior of the balancer housing 17 via the oil discharge holes 45 a, 45 b, and 45 d.

Since the oil outlets 14 b of the oil return passages 14 a are positioned so as to avoid the first and third baffle plates 47 and 49, that is, the oil outlets 14 b face the escape sections 47 a and 49 d of the first and third baffle plates 47 and 49, it is possible, without making the first and third baffle plates 47 and 49 especially compact, to smoothly return to the oil pan 15 oil that has been discharged via the oil outlets 14 b while suppressing interference from the first and third baffle plates 47 and 49. Moreover, since outer edges of the first and third baffle plates 47 and 49, which include positions surrounding the escape sections 47 a and 49 d, are bent downward, it is possible to yet more smoothly return to the oil pan 15 oil discharged via the oil outlets 14 b by guiding it downward.

Furthermore, since the escape section 47 a of the first baffle plate 47 is formed between two bolts 32 via which the first baffle plate 47 is fixed to the balancer housing 17, even when fastening bosses for the bolts 32 are sufficiently thick, the fastening bosses do not project into the escape section 47 a, and the rigidity with which the first baffle plate 47 is secured can thereby be enhanced. Similarly, since the escape section 49 d of the third baffle plate 49 is formed between two bolts 50 via which the third baffle plate 49 is fixed to the lower block 14, even when fastening bosses for the bolts 50 are sufficiently thick, the securing bosses do not project into the escape section 49 d, and the rigidity with which the third baffle plate 49 is secured can thereby be enhanced.

As is clear from FIG. 17, since the innermost end p of the escape section 47 a of the first baffle plate 47 is positioned between facing ends of the two oil discharge holes 45 a and 45 b that are positioned close to the escape section 47 a, it is possible to ensure that there is a minimum distance from the escape section 47 a to the two oil discharge holes 45 a and 45 b, and it is thus possible to suppress the penetration of oil from the oil outlet 14 b into the oil discharge holes 45 a and 45 b. Furthermore, by increasing the distance between the two oil discharge holes 45 a and 45 b and moving the positions of the facing end portions thereof outside a width W of the escape section 47 a, the effect of suppressing the penetration of oil into the oil discharge holes 45 a and 45 b can be further improved.

Embodiments of the present invention are explained in detail above, but the present invention can be modified in a variety of ways without departing from the spirit and scope thereof.

For example, in the first to the fifth embodiments the first and second baffle plates 47 and 48 are fixed to the balancer housing 17 and the third baffle plate 49 is fixed to the lower block 14, but the positions at which they are mounted may be changed as appropriate.

Furthermore, in the fourth and fifth embodiments the escape sections 47 a and 49 d of the first and third baffle plates 47 and 49 are cutouts, but they may be holes.

Moreover, in the fourth embodiment the diameter of the oil outlets 14 b is set so as to be smaller than that of the escape sections 47 a and 49 d but, as in a fifth embodiment shown in FIG. 20, the diameter of oil outlets 14 b may be set so as to be larger than that of escape sections 47 a and 49 d, or parts of the oil outlets 14 b may be offset from the escape sections 47 a and 49 d.

Furthermore, the shape and the number of the oil discharge holes 45 a to 45 d and 46 may be changed as appropriate.

INDUSTRIAL APPLICABILITY

As hereinbefore described, the present invention can be applied suitably to an engine balancer system having a balancer housing formed by joining an upper housing and a lower housing via mating faces, the balancer housing being disposed so as to face an oil pan beneath a crankshaft of an engine. 

1. An engine balancer system having a balancer housing formed by joining an upper housing and a lower housing via mating faces, the balancer housing being disposed so as to face an oil pan beneath a crankshaft of an engine, and the balancer housing being inclined so that the height of the mating faces varies from one side to the other, wherein the upper housing is provided at opposite side edges thereof with mounts through which bolts run for securing the balancer housing to an engine body, and ribs, which extend parallel to each other, are formed on an upper surface of the balancer housing to connect between the mounts.
 2. The engine balancer system according to claim 1, wherein two balancer shafts are sandwiched and rotatably supported between said upper and lower housings so as to extend parallel to each other, and said ribs are formed to extend orthogonally to and straddle the two balancer shafts.
 3. The engine balancer system according to claim 1, wherein two balancer shafts are sandwiched and rotatably supported between said upper and lower housings so as to extend parallel to each other, and a bolt is provided between the parallel-extending ribs as well as between the two balancer shafts for joining the upper housing and the lower housing together.
 4. The engine balancer system according to claim 1, wherein said mounts are formed to project upwardly from an upper surface of the upper housing, said mounts being abutted against the engine body.
 5. An engine balancer system having a balancer housing formed by joining an upper housing and a lower housing via mating faces, the balancer housing being disposed so as to face an oil pan beneath a crankshaft of an engine, and the balancer housing being inclined so that the height of the mating faces varies from one side to the other, wherein the upper housing is provided at opposite side edges thereof with mounts through which bolts run for securing the balancer housing to an engine body, and ribs, which extend parallel to each other, are formed on an upper surface of the balancer housing to connect between the mounts, and wherein an opening is formed on an upper face of the upper housing at a position adjacent to said ribs, said opening being elongated in an axial direction of a balancer shaft which is arranged in the balancer housing.
 6. The engine balancer system according to claim 5, wherein as said balancer shaft, two balancer shafts are sandwiched and rotatably supported between said upper and lower housings so as to extend parallel to each other, and said two balancer shafts have journals, respectively, said journals being pivotally supported on bearing portions of the upper and lower housing, and said ribs are provided along the bearing portion of the upper housing.
 7. The engine balancer system according to claim 6, wherein each of said two balancer shafts has balancer weights on axial front and rear sides of the journal and said elongated opening is provided sidewardly of one of said balancer weights.
 8. The engine balancer system according to claim 5, wherein a further bolt is provided between the parallel-extending ribs for joining the upper and lower housing together and said elongated opening is arranged side-by-side with respect to said further bolt.
 9. The engine balancer system according to claim 5, wherein said elongated opening is provided in a pair and arranged in an aligned manner in the axial direction of the balancer shaft with said ribs being interposed between the pair of elongated openings. 